Transmission or the like



Mawh 5 1940- v VRfs. co'NDloN I I 2,192,539

' TRANSIISSION 0R THE LIKE www ATTORNEYS March 5, 1940. R. s. c oNDoN 2,192,539

y L TRANSMISSION 0R LIKE l Filed Jan. 15, 1937 Y 4 sheets-.sheet 2 INVENTOR A w02 y i BY. f v M {TORNEY Mmh 5, 1940.

R. s. CQNDQN 2,192,539

TRANSMISSION 0R THE LIKE I Filed Jah. l5, 1937 4 Sheets-Sheet 5 79 62 7@ L@24me Hip/k Fi .3, 185 1.93/84 /9/ 125 ma 118 /23 32a bc INVENTOR l Patented Mar. 5,v 1940 UNITE-D1 STATES PATENT! oFFlcE 6 Claims.

This invention relates to variable speed fluid transmissions and the like; and the principal ob' ject of the invention is to provide a transmission ofthe above type consisting of a fluid pump actuated by a constant speed prime mover, said livering same to a uid motor from which the iluid is returned to the tank; meansbeing pro- 'vided for automatically first increasing the de` livery of the pump toits maximum figure, and subsequently automatically decreasing the displacement of the pistons of the motor in order 'to build up the speed of the motor from a. minimum to a maximum.

Further objectsare to provide a unit as above described in which the parts are so arranged and associated that the prime mover is included within the iloor space required for the tank, thus effecting a saving in the requisite iloor space for the unit; also to provide a unit which is economical to manufacture and has novel and eiicient mechanical and hydraulic features hereinafter.

the accompanying drawings, which villustrate practical embodiments thereof, to enable others familiar with the art to adopt and use the same;

and will summarize in the claims .the essential features of the invention, the novel features of construction, and novel combinations of parts,

for which protection is desired.

InA said drawings:

Fig. 1 is an elevation of the fluid transmission unit showing the arrangement of the parts, and also showing my preferred hand control lever and linkage including intermittent gears for operating the cradles of the pump and motor of the unit.

Fig. 2 is fluid motor of the unit.

Fig. l3 is a transverse section through' the motor unit showing theuniversal joint between the shaft and hub, also the eccentric linkages that control the stroke of the pistons according to the angularity of the cradle. I

Fig. 4 is a side elevation of the motor unit showing one form of control lever.

Fig. 5 is a diagrammatic view showing th'e ec- 50 centric plungerfof the lever lshown in Fig. fl, for

positively locating the lever in various determined positions.

Fig. 6v is a longitudinal section through the( pump unit showing the cradle, shafting, cou- 55- pling, and also the centrifugal supercharging a 1ongitudina1 section through the pump which is applied to the end o the pump shaft.

Fig. 7 ls'a diagrammatic view of the iluid circuit used in the transmission; showingv the valve in normal position. 5 pump drawing fluid from an open tank and de- Fig.8 is a view showing the reversing valve of the fluid circuit in reversing position; and i Fig. 9 is a longitudinal section showing a modiiled and simplified piston construction for the pump or motor of the unit.

In brief, the fluid transmission as shown in Fig 1 comprises a prime mover |03 which may bean electric motor, driving afluid pump |30 associated with a 4iluid tank- I 02, and a iluid l, motor I0 operated by the pump IUD through a 15 Suitable fluid circuit. There is a general Similarity between the pump and motor. For convenience I will rst describe the motor unit.

The motor unit In said drawings( Figs. 2 and 3) I0 designates the motor unit casing partly closed at end Illa. At this end Illa a cover plate I5 is applied and sealed by gasket I 6, and having a shaft opening provided with a gland for packing l1. An annular bearing cap II is secured by screws (not shown) to the other end of the casing and sealedby -gasket I2; and a closure plate I3 sealed by gasket I4 is applied to cap II. Cover plates I3 and I5 are held in place by screws I8-I8a or the like. v

Cylindrical valve bushings I9 and 20 are sealed in the bore of cap I I and in the partly closed end Illa of casing I0 respectively, the .bushing I9 containing valve ports 2|, 22, and bushing 20 containing ports 23 and 24. Duets 22 and 23 are interconnected within thecasing I0 by ducts 344i,

`pipe lead 344a (as shown more particularly in Fig. 7.

A shaft 30 provided with a cylindrical bearing surface 30h is journaled in bushing 20 and the outer end of said shaft is bored to receive an inverted coupling sleeve 3l which is keyed and held in position within the bore of shaft 30 by pin 32. The inner end of shaft 30 is machined as at 30a to receive a head 33 which is keyed in position by pin 30a: and secured thereon by axially disposed bolt 34 locked against rota.- tion by lock-Washer 35, the head .33 forming a cylindrical bearing surface. journaled in the valve bushing I9.

Within casing III around shaft 30 is an annular '55 cally opposed pins 8| journaled in corresponding' cradle 25, adjustably supported as hereinafter described with respect to the axis of the shaft. Cradle has an internal annular rib 25a Within which is mounted a hub formed of two annular sections 21-21a interfltted at their meeting faces, said hub 21-21a being disposed around a reduced central portion of shaft and maintained in spaced relation with respect to cradle 25 by roller bearings 26, 26a so that said hub may rotate freely in any position to which it is adjusted by the cradle.

The hub 21-21a is rotated by and with shaft 30 through a universal joint connection, shown more particularly in Fig. 3, and which consists of an elongated member 46 housed in a transverse bore 30c in shaft 30, and provided with diametribores 30d in said shaft. Member 46 has cylindrical ends 80 entering registering bores 21h in the hub members 21-21a to effect a mechanical rotary drive between the hub and shaft, while positioning shaft 30 longitudinally of casing 0.

In.the event shaft 30y and the hub 21--21a y should not rotate coaxially the pins 80 and 8| may adjust themselves longitudinally in their respective bores and thus compensate for any misalignment, allowing the hub and shaft to rotate.

on slightly offset axes without binding.

In the inner ends of the bearing surfaces of shaft 30 and head 33 are sets of opposed cylinders 4| and 38, said cylinders being disposed at a slight angularity to the axis of shaft 30, and having their inner ends terminating opposite the ports 2|, 22, 23, 24 of bushings |9 and 20. Valve ports 36 in head 33 connect the cylinders 38 with ports 22, 2| in bushing I9, while similar valve ports 36 connect the cylinders 4| in shaft 30 with ports 23 and 24 in bushing 20.

Within each of the cylinders 38 and 4| are pistons 29 having pocketed seats 29a for receiving the spherical heads 28a of piston rods 28. p Piston rods 28 also have spherical heads 28o on their outer ends engaging pocketed -seats in bores 21e provided in the sides of hub members 21-21a whereby the piston rods being thus seated in their pocketed bearings cannot become dislodged, thereby dispensing with the necessityof utilizing extraneous means for holding the piston rods 28 locked in their bearings.'

Means are provided for altering the angularity of cradle 25 for the purpose of varying the stroke of pistons 28. As shown in Fig. 3 casing I0 is closed on one sideby a plate 63, sealed by gasket 64, and carrying a pivot 61. A plate 65 is secured to the other side of casing 0, sealed by gasket 66, and carrying pivot 68. Cradle 25 is supported by cradle blocks 69 and 69x fastened by screws 10 to the cradle, the blocks also having -ribs 69g positioned in groove 25g in the cradle; the blocks having bores receiving the pivots 61-68 respectively. A shaft 6| is journaled in plate 66, sealed by packing 1|, and having an operating lever 60 on its outer end, and carrying on its inner end an eccentric ;pin 6| a engaging a slide block 62 confined in a recess 69a in cradle block 69 whereby rotation of shaft 6| will .tilt the cradle 25 with respect to shaft 30 and thereby vary the stroke of pistons 29 which inversely alters the speed of rotation of shaft 30 for any given volume of fluid passing through the motor. 'Ihe use of the slide block 62 in the recess 69a of cradle block 69 engaged by the eccentric pin 6| a of shaft 6| forms a very simple and efficient means for effecting the pivoting of the cradle 25 in order to control the strokes of the pistons.

, tric projection 12b on the inner end of a slidable and rotatable pin 12 which carries knob 15, said projection being adapted to engage any one of a series of staggered holes 65a in plate 65 disposed in two rows (Fig. 4). Spring 13 around pin 12 interposed between arm 60 and a collar 12a on the pin serves to yieldably urge the projection 12b into hole engaging position. A key 14 mounted on lever 60 cooperates with longitudinal slots in the periphery of collar 12a and serves to position pin 12 so' that the projection 12b will engage its proper hole 65a. Hand lever 60 is positioned by pulling knob 15 outwardly until collar 12a is disengaged from key 14 which operation withdraws projection 12b from its hole 65a in plate 65. Knob 15 is then rotated to the desired fractional position as indicated by the numbers 15g: on knob 15, and the hand lever then moved to the approximate location desired as indicated by the position of pointer 60a on lever 60 with respect to the indicia 6512 on plate 65. When knob 15 is released and lever 60 shifted slightly to either side of the approximate location, the key 14 will position pin 12 so that projection 12b will engage its proper hole 65a and accurately position pin 12, and spring 13 will hold the projection 12b in place. Fig. 5 shows four positions of pin 12 relative to lever 60 and indicates that the projection 12b must be in line with a row of holes 65a when key 14 has engaged a slot in collar 12a. These four positions of pin 12 serve to locate and retain lever 60 in definite fractional positions, the relative positions that lever 60 takes in Fig. 5 on graduations 65h on dial 65e being indicated by lines ab, ed, ef and gh, as pin 12b takes the positions 12s, 121', 12q and 12p, respectively.

In the manufacture of the motor, valve bushings |9 and 20 can .be pressed in place in cap and housing |0a respectively, and the end cap then bolted securely to housing l0.' Also shaft 30 and its head 33 can be assembled and locked together by screw 34 and machined to perfect cylindrial form and to a size that will just enter the prepared bores in bushings I9 and 20. Thus, the fluid seal between bushing 20 and shaft bearing 30h; and between bushing |9.and head 33 can be prepared with a marked degree of accuracy, and the parts then partly disassembled to permit-final assembly of the unit.

Screw 34 is drilled at 45 to convey any fluid whichleaks past the fit between I9 and 33 into the bore 30o for universal joint member 46, and` any fluid at that point is driven by centrifugal force finto ducts 41m-41 in the hub to lubricate the heads 28h of the piston rods. Part of fluid which leaks past the fluid seals between cylinders 384| and pistons 29 collects in annular grooves 29x in the outer walls of pistons 29 and is convey'ed through ducts 48 to lubricate the heads 28a of the piston rods. Duct 19 (Fig. 3) isarranged to convey any fluid that may leak past packing 1|, and duct 18 (Fig. 3) is provided to` convey away any fluid that leaks beyond the fluid seals within the motor in order to prevent any churning action on such fluid which would otherwise result when operating at high speeds.

The pump u'm't ing surface journaled in valve bushing |20 which and the structure is generally similar to that l the pump end iiange |84 secured to the housing latter is provided with ducts |23 and l|24 similar to that of bushing 20 of Fig. 1. The shaft is also provided with a cylindrical head |33 secured by bolt |34 and key |302: to the end of shaft |30, said head being journaled in valve bushing ||9 provided with ports |2|, |22. In the bearing portions of the shaft |30 and head |33 are cylinders |4| and |38 respectively, provided with` ducts |36 respective-ly connecting the inner ends of the cylinders with the ports |23, |24, |2|, |22 of the bushings |20 and ||9 respectively, in the same manner as previously described with respect t the corresponding motor parts.

The pump is also provided with a cradle |2`5 pivoted in the casing similarly to the motor -cradle 25, said pump cradle carrying the hub |21|21a supported by roller bearings |26, |26a; and the hub is provided with cylindrical recesses 121e for the heads of the piston rods |28 of pis- Hub |21-'I21a is driven by shaft |30 through a universal joint having pins such as il similar to those of the joint of the motor. Thus the construction and operation of the cradle, pistons, and shaft of the pump are similar to the corresponding parts of the motor, previously de scribed. The pump unit, like the motor unit, has

|00 by screws (not shown) and sealed with gasket |9|. Cover plate |85 is secured to plate |84 with screws |02 and sealed by gasket |93.

The pump unit, however, is provided witha supercharging centrifugal pump |83 (Fig. 6) which is housed between bushing H3, and cover` plate |85, the same being securelyY mounted on head |33 of shaft |30 by screws |81. The pistons |29 of the pump do not act to draw oil into the cylinders |38|4| since centrifugal pump |83 functions to force oil into the suction side o f bushings and I 9 by pumping oil along ducts |88, |8811, to port |2| in bushing H9, and through ducts |90, |9011 and |90c to port |23 in bushing |20. Port |22 is connected by duct 326er to outlet pipe 326, while port |24 is connected by duct 3261) to outlet pipe 326, as shown in Fig. 7,

` through which the pumped fluid is discharged.

In the pump unit the uid pressure developed by the centrifugal pump |83 holds pistons |20 against the connecting rods |28 and keeps the piston rods seated in their bearings. The centrifugal pump is especially desirable because of its quiet operation and inherent characteristic of attaining its own limit of pressure without the need of an auxiliary relief valve.

The structures of both the motor and pump I units are designed for ease in disassembling. Disassembling can be accomplished without removing casings |0 or |00 from their mountings. Disassembly in bothV units is effected similarly, In the case of the motor, this is accomplished by first removing plates 63 and 65 (Fig. 3) and then removing pivot blocks 69 and 693:, and then removing those parts that support bushings I! or 20 in one structure. In the case ofthe pump unit the pump cover |85 must be removed to disengage the centrifugal pump |83 from its mounting on head |33. The cradle |25 may then be removed and shaft I 30 together with all intervening parts can b e drawn'out through the bore |00f as a unit.

Convenience of disassembly and reassembly is a vital factor in servicing as well as manufacture, and coupling 3| is so arranged to permit this method of disassembly. Shafts 30 and |30, being provided with inverted couplings 3| save considerable oor space over conventional types of'A drives having externally applied couplings. The

' space saved is approximately $41 the over-all length of the pump.V or motor units. Theflength or dimensionalong the axis of the drive shaft is the most important dimension, as the electric motor or machine driven by the uid` motor is in most cases of such lateral size that there is considerable lateral clearance to accommodatethe .1 f

motor or pump units. My coupling 3| is' especially designed to allow disassembly of'the pump or motor without removing casings I0 or |00 from sliding t in themotor drive shaft. Thus it is seen that pin 32 is of very `simple character, yet it keys coupling 3| and holds it in place; also permits compensation for misalignment since it is able to rotate in the hole in which it is mounted in. shaft 30 or |30. As this pin is assembled before the motor shaft is brought into place, it has the further advantage of being automatically locked in place by the motor shaft. f I' y As the transmission in .nearly every case is driven by an electric motor the actual iloor space that the user must plan for is that required for the transmission plus that for the electric motor. InV my unit the electric motor |03 is included in the same floor space occupied by the transmis# sion; thus a considerably less amount of floor space is required.

The fact that the fluid connection for a complete transmission can be made by drilling the housing and connecting the pump and motor with ducts which do not require swivel connections, is a definite advantage in economy and provides a reliable construction.

`The fluid transmission Both' the pump and motor units are ange mounted, i. e., secured inplace by `flanges at three points, such as shown at |00, |0d and |0e (Fig. 3) so that regardless of the condition of the surface upon which the pump or motor is mounted, a twist or cramp will not be set up in the casings I0 or |00, as would otherwise be set up if more than three fastening points were used and either the surface of the unit orthe surface upon which it was mounted was not a perfect plane. The twist or cramp due to mounting is' particularly objectionable for a fiuid unit, because the cylindrical fit between shafts 30 and |30 and their valve bushings is so close that any small amount of twist or cramp inthe casingswill cause the parts to bind and prevent free rotation.

'I'he position of the pump in the unit (Fig. 1) is such that the supercharging centrifugal pump |63 of the pump is disposed adjacent the bottom of sump tank |02 with the impeller blades 'disposed parallel with the bottom of the tank so asto be continually primed by the liquid in the tank.

|04 (Figs. l, 7 and 8) designates the reversing on a shaft 2| I journaled valve of the transmission unit, and its handle. The fluid connectionsbetween the pump and motor Iin the transmission unit are shown and, explained with Figs. 7 and 8.

. cooperating with dial 2|5.

to position 2 I 5c.

Shaft 2| I- carries an intermittent gear 2|6, whereby during the motion of lever 2I0 from its normal zero position shown in Fig. 1 to its midposition (2|5b on dial 2|5), the intermittent gear 2|6 will rotate .and drive an intermittent gear 2|1, on shaft |6| of the pump cradle adjusting means, and thus the pump cradle |25 will be rotated on its pivots |08' from the minimum stroke position (shown in Figjl) to a posi"- tion to impart a greater stroke to the pump pistons |29, the eccentric `pin |6|a of shaft I6! engaging the slide block |62 in the cradle block; |69 which is secured to the cradle I 25 in the same manner as the cradle block 6.9, block 62, and pin 6| a of shaft 6I shown in Fig. 4 operate. Further rotation of lever 2|0 in the same direction will bring the cylindrical portion 2|6c of gear 2|6 into engagement with the arcuate portion 2|-1a of gear 2|'|, and will thereby lock the gear 2|1 in such position while lever 2|0 is being shifted from the position 2|5b of dial 2i5 Thus during the first half of the movement of lever 2|0 the pump cradle |25 is tilted to increase the stroke of the pump pistons |29 from the minimum to the maximum.

During the same first h alf of the movement of hand lever 2|0 the cylindrical surfaceZic maintains an engagement with the arcuate portion thus locking Lthe intermittent gear 2|9 ofthe motor against rotation. The second half of the movement of hand -lever 2| 0 moves the motor cradle 25 from its normal position of maximum tilt (shown in Fig. 1) to a position of minimum tilt, for when the lever 2|0 is shifted into dial position 2|5b, gear'tooth 2|6b engages s'lot 2| 9b, and While lever 2|0 is moved from position 2|5b to position 2|5c, gear 2| 9 is rotated therewith. Thus intermittent gear 2|9 rotates shaft 6| of the motor cradle control to shift pin Gla and move slide block 62 in cradle block 69 and thus -rotate the motor cradle 25 about its pivots 68 to a position of less tilt.

The normal position of tilt of pump cradle |25 shown in Fig. 1 represents that at which a low delivery of fluid is pumped. This low delivery when passed through the motor with the motor cradle 25 in the vposition of greatest tilt (which would require a large displacement of pistons 29 for each rotation of shaft 30) results in a low rotational speed imparted to the motor shaft 30 of the transmission; and therefore in such position the constant speed motor |03 of the pump would operate to rotate motor shaft 30 at the latters lowest speed. The fluid circuit of the transmission unit contains a relief valve 325 conf nected in the duct which leads from the delivery side of the pump, said relief valve protecting the pump 'from overload, and since this relief valve 325 also limits 'the pressure obtainable from the pump it isa, factor in limiting the horsepower lever 2| 0 can only act to 2|9a of the motor cradle shifting means,

aioaees speed of rotation of the motor shaft 30 is accomplished by first increasing the delivery of the pump to its maximum figure, the horsepower delivery from the pump can therewith be increased to its maximum figure. It is for this reason that the intermittent gears 2|8, 2|'| and 2 I 9 are employed in my transmission, so that the first half of the rotationof hand lever 2| 0 will function to increase the delivery of the pump without altering the displacement of the pistons 29 of the motor unit. As the rst half of the rotation of lever 2|0 has effected an increase in R. P. M. of motor shaft 30 by increasing the delivery of the pump to its maximum amount, the second half of the rotation of this decrease the displacement of the motor pistons 29 to further increase the speed of the motor shaft.

Figs. 7 and 3 illustrate the fluid connections between. the tank |02, pump |00, and motor |0. This 'circuit is a so-called open fluid circuit since the fluid is taken from the open tank |02,

as explained above, by the centrifugal pump |83 and forced into the pump pistons |29, and from to from the motor to the open tank |02 again.

Fig. 7 indicates six cylinders in the shaft |30 of the pump and .in the shaft 30 of the motor displaced 30 with respect to the six cylinders in the head |33 of the pump and head 33 of the motor respectively. Thus the delivery of the cylinders in the groups is staggered so that there will be twelve impulses for each revolution'. Theeven number of cylinders in each group maintains three pressure cylinders in each group at all -times so that the end thrust is constant in amount and is balanced by the end thrust of the three pressure cylinders in the opposing cylinders. That portion of the drawing shown in Fig. 7 by dotted lines represents the side of the pump and motor that is under supercharging or exhaust pressures respectively, and the portions shown in solid lines represent the sides of the pump and motor thatare under operating pressure. Thus as shown, the cylinders I4Im and |4In'and |4|p in pump shaft |30, and cylinders |381, |385` and |381? of pump head |33 are on the supercharged side of the pump.

Fluid is pumped under low pressure from the sump |02 by the centrifugal pump |83 (not shown) and conveyed through ducts |90, |90b, and |90c to port through ducts |88, head bushing -||9. inders I4Im, The cylinders I4Iu, I4IU, I4Iw, of shaft |30l and cylinders |382, |381/ and |3821,- of pump head |33 are on the pressure side of the pump, and fluid from these cylinders is delivered to ports |24 and |22. From port |24 the fluid is transmitted along duct 32611 and 326 to the chamber |04a of reversing valve |04. From port 22 the iiuid is transmitted along ducts 326a and"328 to chamber |04a oi valve |04. If the uid v`rises in pressure above a definite maximum pressure `it will be allowed to escape along duct 325 and back to the sump |02 by raising ball 325b from its seat and compressing spring 325e. Fluid from valve |88a to port |2| of the pump Thisuid enters the cyl,l

Mln, HID, |381', |388, and |38t.

chamber l 04a (in the position of the valve shown in Fig. 7) is conducted under pressure to the receiving side of the motor through ducts 344a and 3441 and to port'2| of motor bushing I9,

- and by way of ducts 324a and 324c7to port 24 of of its chamber as shown in Fig. 8. In this position of the valve, chamber |04a. connects duct 326 to duct 344d; and chamber |04b connects duct 344a to duct 321. 'I'hus the normal exhaust -side of themotor becomes the pressure side,

and the normal pressure side of Athe motor becomes the exhaust side.

Any air in the circulating fluid escapes in the open tank |02 by rising tothe top thereof, and

i same is not recirculated through the `transmission, resultingA in a quiet operating unit. The motor discharges only against atmospheric pressure and is not required to overcome back pressures, and thus the peak pressure of the transmission can be reducedby the amount of back pressure for a given power transmission. The heat'generated in the fluid is dissipated through the walls of the sump upon return thereto of th fluid.

In operation In the normal position of lever 2| 0 (Fig. 1), the pump cradle |25 is in its minimum tilt position, while the motor cradle 25 is held `in maximum tilt position'by engagement of arcuate surface 2|6c of gear 2|6 with the concave portion 2 |9a of gear 2|9. When valve |04 is in the position shown in Fig."1, and prime mover |03 is actuated, pump shaft |30 (and head |33) is rotated in a counter-clockwise direction as shown by the 'arrows in Fig. 7, so that the pistons in pump ushaft |30 to the left of the vertical in Fig. '1, and the pump pistons in head|33 to the right of said vertical, will be discharging. Centrifugalh pump |83 delivers fluid from'tank |02 into ports |23 and |2| of the pump, which uid enters the cylinders and is carried around and delivered through the ports |24 and |22 to the outlet duct 326 leading to the port |04a, valve |04, relief valve '32511 limiting the pressure of the fluids.

'Ihe fluid from Valve port |04a passes through duct 344a into the ports 24 and 2| of the motor rotating the motor shaft 30 (and head 33) in the direction of the arrows (Fig. '7), the fluid being discharged through .ports 23 and 22, ducts 344k, and 344d, valve port |04c, and pipe 321 back into tank |02. If, however, valve |04 is shifted into the position shown in Fig. 8, the direction of' rotation of the motor shaft 30 is reversed, since duct 344d then becomes the fluid feed duct,

and duct 344a the uid discharge duct of the motor.

Since `th'e six cylinders in each of the shafts |30 and 30 are displaced 30 with respect to the six cylinders in each of the heads |33 and 33 of the pump and motor respectively, there will be twelve uid impulses instead of six for each revolution thereby providing double displacement and double the number of impulses, while permitting use of shafts of minimum diameter and consequent use of valve housings of minimum diameter and also providing minimum peripheral of its movement, pump cradle |25 is rotated from .its position of minimum'tilt to' its position' of maximum tilt, while the motor cradle 25 is maintained at its position of maximum tilt, and thus during such movement the volume of fluid delivered by the pump to the motor is increased to its maximum amount developing the horsepower of the pump and at the same time eifecting increase in the motor shaft speed by` increase in fluid circulation. Further movement of lever 2|0 merely acts to decrease the displacement of the motor pistons, thereby further increasing the speed of the motor shaft.

Modification Fig. 9 shows a simplified embodiment vof the motor unit, the construction being also equally applicable to the pump unit. Parts I0; ll, 1, 9, 20, 25, 26 and 26a are identical to those shown in Fig. 2 and function in the same manner. Pis- 2 tons 429 engage'the sides of hub 421-421a directly without utilizing intervening piston rods (such as -rods 28 shown in Fig. 2), the outer ends of pistons 429 engaging the curved surfaces 421b and 421e of hub members 421-421a. This method of engagement promotes rotation of the pistons 429 in their cylinders while the pistonsoperate through their strokes, the pistons rolling along the ,curved surfaces 421b-421c of the hub. During this period of engagement the pistons contact on their sides so-that the relative radial contact acts to rotate the pistons .in their cylinders.

In this modification the universal joint (shown in Fig. 3) is not used. l The hub 421-421a is free to rotate, and is in fact driven rotatively by'. the action of pistons 429. 421d and `421e are notches serving as wrench keys when hub members 421 and 421a are fastened together by threads 421f.

4Shafts 430 and 433 are held longitudinally by end plates 450 and 4|3 which engage bearing surfaces 450a and 4|3a respectively. Any fluid leaking past the seal between bushing I9 and l head 433 enters bore 45 in bolt 34 and is conveyed by centrifugal force to bearings 26 and 26a along ducts ma, 4301 and 421g. Any fluid leaking 50 past the seal between shaft 430 and bushing 20 is carried back'into the housing by` duct 445a. The valvey operation, `control 'and general arrangement when using pumps or motors of the type shown in Fig. 9 is similar to that previously described with respect to Figs. 1-8.

I claim:

1. In combination, a casinghaving an4 open end and having a partly closed end forming a bore; an annular cap of substantially same diameter as the casing closing. the open end of the casing and forminganother bore; cylindrical bushings in said bores having valve ports connected in a fluid circuiti a shaft having one end entering the casing and having cylindrical enlargements journaled in said bushings; a hub of less diameter than the open end of the casing surrounding the shaft between the bushings; removable supports for the hub; opposed sets of cylinders in the shaft at opposite sides of the hub having ducts registering with the valve ports; pistons in said cylinders engaging the hub and centering the shaft in the bushings; and means for tilting the hub to vary the strokes of the pistons; whereby when the supports and annular cap are removed the shaft assembly may be Withdrawn as a unit through the open. end of the casing.

2. In a combination as set forth in claim l, said cylinders being disposed obliquely to the axis of the shaft 'and disposed Within the cylindrical enlargements; said shaft having an enlargement intermediate its ends Within the hub provided with a transverse bore; a pin extending through the bore and having its ends slidably engaging opposed recesses in. the hub; and a member transflxing the pin normal'to the axis thereof and maintaining the pin in the bore whereby the hub will be rotated by the shaft.

3. In a combination as set forth in claim l,

' said supports comprising a cradle pivoted in the casing carrying the hub; a block carriedby the cradle -having a recess; a slide reciprocably mounted in the recess; and said tilting means comprising a rock shaft journaiecl in the casing having an eccentric member engaging the slide; and means for rocking the rock shaft.

4. In combination, a casing having an open end and having a partly closed end forming a bore; an annular cap of substantially same diameter as the casing closing the open end of the casing and forming another bore; cylindrical bushings in said bores having valve ports connected in a uid circuit; a shaft having the end entering the casing and having a cylindrical enlargement ;lournaled in one bushing; a removable cylindrical head on said shaft journaled in the other bushing; a hub of less diameter than the open end of the casing. surrounding the shaft between the bushings; removable supports for the hub; opposed sets of cylinders inthe shaft and head at opposite sides of the hub having ducts annabee registering with the valve ports; and pistons in said cylinders engaging the hub and centering the shaft in the bushings; whereby when the supports and annular cap are removed the shaft assembly may be removed as a unit through the open end of the casing.

5. In combination, a casing having an open end and having a partly closed end forming a bore; an annular cap of substantially same diameter as the casing closing the open end of the .casing and forming another bore; cylindrical bushings in said bores having valve ports connected in a fluid circuit; a shaft having one end entering the casing and having cylindrical en largements journaled in said bushings; a hub surrounding the shaft between the bushings; opposed sets of cylinders in the shaft at opposite sides of the hub having ducts registering with the valve ports; and centering the shaft in the bushings; pistons in said cylinders engaging the hub; said casing having removable side plates carrying aligned trunnions; a cradle of less dameter than the open end of the casing pivoted in said trunnions and carrying the hub; and means for tilting the cradle to vary the stroke of the piston; whereby when the side plates, and annular cap are removed the shaft assembly including the hub and cradle may be removed through the open end of the casing.

6. In a combination as set forth in claim 5, said tilting means comprising a block carried by the cradle having a recess; a slide reciprocably m'ounted in the recess; a rock shaft journaled in one side plate having an eccentric member engaging the slide; and means for rocking the rock shaft.

ROBERT S. CONDON. 

